KR100460195B1 - A burner system reducing air-polution material - Google Patents

Abstract

The present invention relates to a burner system that can completely reduce the air pollutants by the complete combustion, a blower for blowing air for combustion, three cylindrical ports having the same central axis and different radii, both ends of each port A flat disk supporting the port, an air nozzle for injecting combustion air into the burner, a cylindrical emulsion injector formed in the center of the burner, and a waller that provides rotational force to the combustion air. When the air is tangentially blown into the outer port, the air is cooled by air by rotating the space between the ports, and the temperature is raised.The air is sprayed into the burner through the air nozzle installed in the inner port and hit the outlet disc. Some of the bumped air is returned to the inside of the burner to become the primary combustion air and the rest is out. It flows through the disc to the outlet and becomes the secondary combustion air, and the primary combustion air is returned by the waller to surround the emulsion injector, and then mixed with the fuel injected from the emulsion injector to completely burn the air pollutants. There is provided a burner system that is dramatically reduced.

Description

Burner system for reducing air pollutants {A burner system reducing air-polution material}

The present invention relates to an industrial burner system capable of dramatically reducing air pollutants such as dioxins, carbon monoxide (CO), nitrogen oxides (NOx), and sulfur oxides (SOx) by completely burning fuel. In particular, it relates to a burner system using waste oil or waste oil refinery oil as fuel, and in particular emulsion fuel oil prepared by adding water thereto.

In the conventional burner, various methods for reducing air pollutants have been proposed, and in particular, the inventions and designs for reducing NOx have become mainstream. The following outlines the prior art and extracts the problems.

First, to reduce the NOx by adjusting the spiral air dispersion plate to maintain the optimum combustion state according to the combustion conditions (registration number 20-0236493, 'low nitrogen oxide burner', 'advanced technology 1'). There is). 13A, combustion air injected through the outer turning vane 3 and the inner turning vane 4 becomes faster by passing through a passage formed narrower in the furnace direction, and thus the supplied combustion air As a result, the fuel injected from the fuel nozzle (2) generates heat from the flame (1) while generating heat, and so far, it is a traditional burner. 'First technology 1' is a secondary smoke formed by adding a spiral variable air dispersion plate (5) and a diffusion separator (6) to the primary combustion air formed in front of the flame opening and the flame opening. It is intended to supply properly divided into the required air. This enhances the flame retardancy and creates a high temperature internal circulation to suppress the generation of nitrogen oxides.

Secondly, the exhaust gas and combustion air are directly heat-exchanged in the heat storage body to reduce NOx (registered number 10-0230940 'low NOx burner', 'prior art 2'). 'Previous technology 2' is a high temperature combustion air is sufficiently injected into the central clearance 24, as shown in Figure 13b, the outlet is connected to the expansion portion 23 surrounded by the burner tile 22, this expansion The neck is larger in diameter than the central clearance 24. The fuel injection nozzle 19 is provided in the enlarged diameter part. The diameter-expansion part 23 is for underpressure by the flow of the combustion air blown off from the center clearance tube 24. This causes a strong exhaust gas recycle in the furnace due to the negative pressure applied to the subcombustion chamber 25, and thus, the flame holding zone X1, the furnace exhaust gas recirculation combustion zone X2, and the gentle combustion zone X3 are formed. By doing so, it is possible to realize low NOx and to improve the stability of the flame.

Third, the combustion air is ejected from the central clearance of the burner, and the fuel is injected into two stages of the primary nozzle and the secondary nozzle around the burner to form a primary flame and a secondary flame. In order to reduce the NOx by supplying sufficient air and inducing the reaction between the secondary fuel and the primary flame high temperature mixer in the secondary flame to reduce the oxygen concentration so that the reduction reaction can occur (Japanese Patent Laid-Open Publication No. 6-50508, 'Prior Art' 3 ') is introduced. Prior art 3, the primary fuel nozzle 32 and the secondary fuel nozzle 33 formed between the burner tile 31 in the high-temperature combustion air supplied through the central clearance (A), as shown in Figure 1c Inject the fuel from the primary fuel nozzle 32, and the fuel injected from the primary fuel nozzle 32 is mixed with a large amount of air supplied from the central clearance A to form the primary flame in the excess oxygen state, and again the secondary fuel The fuel injected from the nozzle 33 is mixed to form a secondary flame in which a reduction reaction occurs due to low oxygen concentration, thereby realizing low NOx.

Fourth, concentric retardant gas supply pipes are provided outside the fuel supply pipes leading to the fuel nozzles, and oxygen is used as the retardant gas to obtain a long and large flame and to reduce the amount of NOx generated (registration number 10-0193294, Liquid fuel burners and advanced technology 4). As shown in FIG. 1D, the 'prior art 4' has a concentricity on the outer side of the fuel supply pipe 42 so as to form a retardant gas passage with the fuel supply pipe 42 having the fuel injection nozzle 41 at the distal end. A gas supply pipe 43 was provided, and an orifice member 44 was provided in the fuel supply pipe with a gap from the tip of the fuel supply pipe 42. The orifice 45 of the orifice member 44 and the fuel injection nozzle 41 of the fuel supply pipe 42 are eccentric with each other. Advanced technology 4 is to control the flow rate and flow rate of retardant gas (oxygen) to obtain a long and large flame at high temperature.

The above prior arts have found various problems in burners which are mainly liquid fueled. The addition of the spiral variable air dispersion plate (9) and the diffusion type separation cylinder (6) to the traditional burner in the 'prior art 1' does not mean that strong swirl flow can be formed, and the NOx reduction effect is insignificant. Do.

The leading technology 2 is to make the swirl flow by expanding the passage of combustion air suddenly in the vicinity of the inlet port so that the negative pressure is applied, but in reality, the negative pressure is not only low but also the powerful swirl flow is obtained only by the negative pressure. There is a limit to achieving high efficiency combustion. Accordingly, the effect of reducing pollutants is also negligible.

'Advanced Technology 3' In FIG. 2, the reducing atmosphere in the secondary flame caused by the secondary fuel nozzle is not remarkable, and thus, it is insufficient to realize low NOx.

'Advanced Technology 4' uses oxygen as auxiliary fuel (combustible gas) and adjusts its flow rate and flow rate to obtain high-temperature flames, while pollutants are considerably reduced, but the use of oxygen is expensive and costly. Compared with the prior art related to a method of vortexing combustion air, Japanese Patent Application Laid-Open Method and Apparatus for generating and combusting an oil-and-water emulsion (Japanese Patent Application Laid-Open No. 58-140506, prior art 5). And the Korean Registered Utility Model 'Complete Combustion System for Dry Gas (Registration No. 20-0231928,' Preceding Technology 6 '). It is intended to assist the combustion of the flame 54 by attaching a gas reaction burner 50 to the flame outlet of the conventional oil burner 59, as shown in Figure 13f, the gas reaction burner 50 Inner cylinder (51), air preheat The cylinder 52, the outer cylinder 53, etc. are provided. Blowing air blown in the blower 55 first passes through the space between the outer cylinder 53 and the air preheating cylinder 52 into the space between the air preheating cylinder 52 and the inner cylinder 51, the entered air is It is designed to vortex the flame 54 by direct injection into the gas combustion reactor 50 through a plurality of small holes 57 installed in the inner cylinder. Here, the small holes 57 are scattered in various parts of the inner cylinder 51. This method is meaningful in that it can firstly preheat the combustion air to some extent, and secondly, it is possible to improve the combustion state by making a swirl flame. However, the method of 'prior art 5' has the following problems. First, the preheating of combustion air is not sufficient. Indirect heat transmitted through the inner wall alone is not enough to preheat the rapidly injected air. According to the experimental process of the present invention, the temperature when the combustion air enters the inner cylinder is only about 120 degrees Celsius, the maximum preheating temperature in the prior art (5) is about this, and the flame outlet in the inner cylinder (51) It is clear that the temperature of the air injected into the near hole 57 is lower than this. If so, this temperature is too low to limit the combustion of the flame. At this temperature, the combustion air expands by about 40%, which is also insufficient to turn the flames, and therefore, a lot of air must be added to turn the flames strongly. Since air causes the flame temperature to drop, the combustion condition also does not improve significantly. In addition, the method injects air in addition to the air injected by itself in the conventional burner 59, so that the amount of air is inevitably increased, and thus the problem of the excessive NOx and low temperature flame described above cannot be avoided. In order to preheat the combustion air in the method of the prior art (5), the refractory is not installed on the inner wall of the inner cylinder (51), but the steel plate should be intact. In this case, if the temperature of the flame is very high, the inner cylinder (51) of the iron plate This does not remain. This is because the air curtain cannot be hit on the inner barrel and the flame outlet. The flame according to the present invention has a maximum temperature of 2200 degrees Celsius, but if the prior art (5) is also the inner cylinder 51 is melted away. After all, the method of the prior art (5) says that the flame temperature is 1280 degrees Celsius, which is insufficient to completely burn waste oil or bunker seed oil. In addition, even at such a flame temperature, the inner cylinder 51 is rapidly corroded at high temperature, and in particular, the flame outlet portion of the inner cylinder 51 cannot maintain durability. Fifth, in this method, only the flame ejected from the conventional burner is used. It is difficult to achieve complete combustion because it turns in the empty space in (51), and in particular, there is a problem that soot, which is incombustible, accumulates on the lower end of the inner cylinder 51 and needs to be frequently cleaned. In particular, when the waste oil is used as the combustion oil, non-combustible materials such as powder or lime contained in the waste oil accumulate on the lower end of the inner cylinder 51, which causes the combustion state to deteriorate rapidly. In the present invention, the reason why the emulsion injector 130 is installed in the center of the inner cylinder is to solve this problem and lead to complete combustion. Domestic registered utility model 'Drying gas complete combustion device (Registration No. 20-0231928,' prior art ' 6 ') is designed to burn dry gas extracted during incineration of waste tires, and includes a primary combustion unit 60 and a secondary combustion unit 70 configured as a castable, and in the primary combustion unit 60, The incomplete combustion of dry gas and flame to the secondary combustion unit is the principle of complete combustion in the secondary combustion unit (70). Here, the secondary combustion unit is composed of a double tube consisting of an outer tube 71 and an inner tube 72, and a wind supply chamber 73 is formed between the outer tube 71 and the inner tube 72, and the inner tube 72. ) Is formed so that a plurality of wind supply holes 74 are inclined at a predetermined angle at regular intervals to vortex at the moment the wind is supplied to the secondary combustion chamber (75). The design of the secondary combustion chamber (75) of this design is meaningful to obtain a swirling flame due to the wind injected thereto. However, this design also has the following problems. First, the air supplied to the secondary combustion chamber 75 is hardly preheated. This is because the inside of the secondary combustion chamber 75 was constructed with refractory materials. Of course, this is a bit of warming up, but very little. As a result, it is difficult to achieve complete combustion because it does not supply enough preheated air. Second, the wind supply hole 74 is provided in the entire inner tube 72 of the secondary combustion chamber 74 to obtain a high-temperature purified flame. And only serves to properly burn dry gas. Third, due to the lack of preheating of the air, the lack of air curtains, the lack of the functions performed by the emulsion injector 130 of the present invention, and the like in the prior art (5). As such, there are problems such as excessive generation of NOx, incomplete combustion, insufficient durability, and accumulation of soot in the secondary combustion chamber.

Although not shown in the figure, the combustion air is dividedly supplied to the inner and outer cylinders of the burner main body, and the outer cylinder air is guided to turn through the turning machine, and the flame is divided into the inner cylinder and the outer cylinder and installed, respectively, to provide powerful swirl The technique of doubling the combustion efficiency and realizing flame safety and low NOx (Public Publication No. 1994-0018602), and the method of injection of liquid fuel, and the internal fuel injection hole in which the fuel is ejected from the center and the space around it And injection through the external fuel injection hole formed, each injection hole is provided with a separate vortex chamber, and by installing different injection angles to form a double flame structure to realize a low NOx (Registration No. 10- 0363765). However, these techniques do not form vortices properly, and there are many improvements in terms of reducing pollutants.

As such, the conventional burner technology does not significantly suppress the generation of nitrogen oxides, which are problematic in fuels such as diesel and bunker C oils, and the atmosphere, such as sulfur oxides, carbon monoxide, and dioxins, which are problematic when fueling waste oil or refined oils. We do not provide adequate countermeasures for the generation of pollutants. In addition, the fuel efficiency is wasted because the combustion efficiency is not high when generating the heat required to operate the steam turbine or Stirling Engine.

The present invention has been made to solve the above problems, and to solve the problems in accordance with the criteria of the following paragraphs.

(1) to form a powerful vortex in the flame generated by the burner to promote the efficiency of combustion

(2) create long and large flames to produce the maximum heat;

(3) The flame temperature can be adjusted appropriately according to the conditions of use, and the maximum temperature is higher than 2,000 degrees Celsius, providing a suitable means for the areas requiring high heat.

(4) Efficiently supply the amount of heat required for the Stirling engine, which has recently been put into practical use,

(5) To provide a burner system with a combustion method that can minimize the generation of air pollutants such as dioxins, nitrogen oxides, sulfur oxides, carbon monoxide, odors, and soot.

In order to achieve the above object, there is provided a burner system for reducing air pollutants.

One port (inner port) for cylindrical burners, at least one other port (space port or outer port when two outer ports are formed) with a space outside the inner port, and a part of the outer port Inlet and blower that blows air to the inlet, and a plurality of air nozzles to shoot air to the outlet side disc in the burner, and to the fuel injection side disc of the burner A wall-type emulsion injector, which is an emulsion supply device that protrudes into the burner from the center of the fuel inlet side of the burner, and injects the swirling air into the burner. A burner system for reducing air pollutants consisting of a number of orifices is available The. In this burner system, the fuel is mainly an emulsion fuel oil made by mixing water with an appropriate ratio of liquid fuel such as diesel oil, bunker C oil, waste oil and waste oil refinery oil. Combustion air is blown in the blower so as to rotate between the outer port and the middle port (or inner port), and the air becomes a vortex to cool the outer port, the middle port and / or the inner port, and to raise the temperature at the same time. It is injected into the burner through the air nozzle installed in the port. In the burner, this air is properly divided into primary combustion and secondary combustion, and the primary combustion air forms a large cylinder inside the inner port and proceeds to the fuel injection port. The wall forms a vortex with proper strength and rotation diameter, which forms a small cylinder, wraps around the emulsion injector, mixes with the emulsion, forms a flame, and proceeds to the outlet, and the flame passes through the outlet for secondary combustion air. It is completely burned with new oxygen supply.

1 is a longitudinal sectional view showing the configuration and air flow of a basic burner according to the present invention;

2 is a perspective view of a burner according to the present invention;

Figure 3 is a front view as seen from the outlet side of the burner according to the present invention,

Figure 4 is a front view showing the relationship that the air is introduced in the blower of Figure 1,

5 is a longitudinal cross-sectional view showing the internal structure of FIG.

6 is a cross-sectional view of FIG.

7 is a cross-sectional view showing the main portion of the A-A line of Figure 1 with the air flow,

FIG. 8 is a cross-sectional view showing only the inner port of the air nozzle part of FIG. 7;

9 is a front view illustrating main parts of the emulsion injector in the emulsion injector of FIG. 1;

10 is a plan view showing the structure of the waller of FIG.

11 is a longitudinal sectional view showing the configuration and air flow of the burner according to the first embodiment of the present invention;

12 is a cross sectional view showing the main portion A-A of FIG. 11 together with the airflow;

Figure 13a is a longitudinal sectional view showing the structure of a burner according to the prior art 1,

Figure 13b is a longitudinal sectional view showing the structure of the burner according to the prior art 2,

Figure 13c is a longitudinal sectional view showing the structure of a burner according to the prior art 3,

Figure 13d is a longitudinal sectional view showing the structure of the burner according to the prior art 4, Figure 13e is a longitudinal sectional view showing the structure of the burner according to the prior art 5, Figure 13f is a longitudinal sectional view showing the structure of the burner according to the prior art 6 .

Hereinafter, the configuration of the present invention will be described in detail by the accompanying drawings.

1 is a representative view of a basic type as a burner system 100 for reducing air pollutants for implementing the present invention. In FIG. 1, the cylindrical outer port 101, the middle port 102 and the inner port 103 are installed to have the same central axis and have different radii, the radius of which is the middle port 102 more than the outer port 101. It is small and the inner port 103 is smaller than the middle port 102. Therefore, a space is formed between the cylindrical curved surfaces of each port. In particular, the space between the middle port 102 and the inner port 103 is narrower than the space between the outer port 101 and the middle port 102. Each port is welded to and supported by the fuel inlet side disc 104 and the outlet side disc 105, with only the middle port 102 being spaced apart without contacting the fuel inlet side disc 104.

The blower blower 111 is installed at the outlet side end of the outer port 101. The combustion air blown by the blower 111 is injected between the outer port 101 and the middle port 102 through the inlet 112, where the inlet 112 is tangential to the curved surface of the outer port 101. Is installed. Therefore, the air injected into the inlet 112 proceeds toward the fuel inlet 106 while rotating the space between the outer port 101 and the middle port 102. In this process, the air is heated while containing heat transferred from the hot flame in the burner, and the outer port 101 and the middle port 102 are air cooled. In this case, the outer temperature of the outer port 101 does not exceed 50 degrees Celsius, which is a temperature suitable for laws related to hot air.

Combustion air, which proceeds while rotating between the outer port 102 and the middle port 102, rotates in a direction while striking the disk 104 on the fuel inlet side. The inflection point that changes direction is made in a space where the middle port 102 and the fuel injection side disk 104 are spaced apart. At the inflection point, it is important to ensure that the combustion air loses torque and does not become turbulent. The combustion air that has passed the inflection point now advances the space between the middle port 102 and the inner port 103 in the direction of the outlet side disk 105, in which a higher temperature is retained, and the middle port 102 The inner pot 102 is cooled by air. In particular, the space between the middle port 102 and the inner port 103 is narrower than the space between the outer port 101 and the middle port 102, the combustion air is rotated at a higher speed by the Venturi principle.

The combustion air approaching the outer disc 105 while rotating is entered into the burner by the air nozzle 107 installed at an inclination of 10 to 15 degrees in the outlet direction than a tangent on the inner circumferential surface in the rotation direction. In the basic type, a plurality of air nozzles 107 are installed at a distance of 45 to 70 millimeters from the outlet side disk 105. Therefore, the portion of the space between the middle port 102 and the inner port 103 close to the outlet side disc 105 becomes a dead space deviated from the path of movement of air, and the combustion air is easily There is a risk of turning into turbulence. Here too, it is important for the combustion air to enter the burner through the air nozzle 107 while maintaining the rotational force.

Air nozzle 107 is best to make a hole to contact the inner wall surface from the outer wall surface of the inner port 103 to the inner wall surface than to install a separate nozzle device. If the air nozzle 107 is made separately and installed, the installation work is difficult and costs more, while the function is not improved. In addition, even if an air collecting device is installed such that combustion air flows easily into the air nozzle 107 from the inner wall of the inner port 103, combustion is not greatly improved. However, when the air collecting device is installed, the pressure of the blower 111 may be less. Therefore, if the pressure of the blower 111 and the thickness of the air flesh rotating from the blower 111 to the air nozzle 107 is properly adjusted, no separate air collecting device is required. The thickness of the air flesh varies not only by the pressure of the blower 111, but also by variables such as the distance between the outer port 101 and the middle port 102, the distance between the middle port 102 and the inner port 103, the length of the burner, and the like. . In FIG. 8, the structure of the air nozzle 107 is shown by showing the thickness of the inner pot 103. As shown in FIG. Combustion air proceeds in the direction of the arrow. Therefore, if the thickness of the inner pot 103 is too thin, it is difficult to make the air nozzle 107 and its function is also poor. In the basic type, the inner pot 103 was made of stainless steel of 10 millimeters.

Combustion air, which has entered the burner through the air nozzle 107, rotates through the inner wall surface of the inner port 103 and goes to the outlet side disk 105 to be hit. It is advisable to rotate at least 360 degrees until the combustion air exits the air nozzle and hits the outlet side disk 105, and the rotational speed to the outlet side disk 105 is the inclination angle of the air nozzle 107. And the distance from the air nozzle 107 to the outlet side disk 105.

Combustion air that hits the outlet side disc 105 has a class that is bent 180 degrees according to the size and structure of the disc and proceeds toward the fuel injection side disc 104 of the burner, and some of the outlet side disc 105 Ride out to the outlet (108). The air that is bent and goes deep into the burner is called primary combustion air, and the air that exits the outlet is called secondary combustion air. Here, the ratio of the primary combustion air and the secondary combustion air is very important, that is, the pressure of the blower 111, the gap between the outer port 101 and the middle port 102, and the gap between the middle port 102 and the inner port 103. , The diameter of the air nozzle 107, the angle of the air nozzle 107, the separation distance from the outlet side disk 105 of the air nozzle 107, and the diameter of the outlet 108. To increase the ratio of the primary combustion air, the pressure of the blower 111 is large, the distance between the outer port 101 and the middle port 102 is small, and the distance between the middle port 102 and the inner port 103 is smaller. The smaller the diameter of the air nozzle 107 and the larger the angle, the shorter the distance from the outlet side disk 105 of the air nozzle 107 and the smaller the diameter of the outlet 108 is. However, there is no optimal value for this ratio. It is better to design differently according to the use of burner. For example, if a long and large flame is required, the ratio of the secondary combustion air should be increased. If a combustion gas having a higher temperature than the flame is required, the ratio of the primary combustion air is increased to increase the ratio of most combustion inside the burner. Should be made.

The primary combustion air should hit the outlet side disc 105 and not lose its rotational force. In the process of changing the direction deep into the burner, a large cylinder is formed. As a result, a large cylinder formed near the inner wall surface of the inner port 103 inside the burner proceeds toward the fuel inlet 106, and the temperature of the combustion air not only rises but also prevents the heat of the flame from spreading. The temperature is protected and maintained, and the inner wall surface of the inner pot 103 is protected from the flame. In other words, the large cylinder of combustion air has the same effect as the air curtain struck between the flame and the inner pot 103. In particular, the air curtain is doubled in the section from the air nozzle 107 to the outlet side disk 105. The air curtain formed by the air from the air nozzle 107 proceeds to the outlet side disk 105 and the large cylinder which collides with the outlet side disk 105 to be bent. Here, the large cylinder does not rotate while rubbing against the inner wall of the inner pot 103 by centrifugal force, but rotates by its own rotational inertia. In addition, a space is formed between the inner nozzle 103 and the large cylinder from the air nozzle 107 to the fuel injection side disk 104. Therefore, there is no load applied to the inner wall surface of the inner port 103 and the pressure drop phenomenon and the rotation force drop phenomenon due to the friction force do not occur. That is, it does not matter even if the inner wall surface of the inner pot 103 is not smoothed.

The large cylinder of combustion air is changed back by the wall 120 installed on the fuel injection side disk 104 and becomes a small cylinder to proceed toward the outlet 108. The rotational force of the small cylinder is doubled and the small cylinder is induced to rotate around the emulsion injector 130 extending toward the center of the burner. Waller 120 has a shape or the edge of the edge is similar to the rotating plate installed on the bottom of the washing machine serves to prevent the air for combustion is scattered. In the center of the wall 120, a round space is formed so that the emulsion injector 130 can be installed. The waller 120 is electrically operated by the motor 121 at the bottom thereof.

The small cylinder of combustion air surrounds the emulsion injector 130 and mixes with the emulsion ejected from the emulsion injector 130 as a dome, thereby effectively supplying oxygen to induce a good combustion state. In addition, the small cylinder combustion air contains a sufficiently high temperature and rotates, thus achieving high temperature combustion and evenly supplying oxygen to the flame to maximize combustion efficiency. Initial combustion takes place through ignition 140.

The combustion air gradually rises in temperature until it flows into the inlet 112 and is returned by the waller 120. According to the measurement data for the basic burner according to the present invention, at the moment when air at 22 ° C. enters the space between the middle port 102 and the inner port 103 in the inlet 112, the air nozzle 107 At the moment of entering, it became 127 ° C., and when the air injected from the air nozzle 107 hit the outlet side disc 105, the temperature rose rapidly to about 250 ° C. and hit the outlet side disc 105. The air coming down to the fuel injection side disk 104 and hit the wall 120 became about 780 ° C. The flame is 1300 ° C-1500 ° C at the end of the emulsion injector 130 and 1600 ° C-2200 in the case of the flame exiting the outlet 108 when an emulsion made from 75% waste oil refinery and 25% water is used as the fuel. The temperature in ° C. was recorded. The temperature is also affected by the blowing amount of combustion air, the addition ratio of water, and the like.

Increasing the temperature of the combustion air means that the volume of the combustion air is gradually increased. This is because when the temperature increases, the activity of gas molecules becomes active, and thus the density of air becomes thin and the volume expands. The above table summarizes the ratio of temperature and air volume for each stage of combustion air. In this table, the ratio of volume is calculated by setting the temperature of 22 ° C., which is initially introduced through the inlet 112, to 100.

In the above table, the volume of combustion air is 3.65 times larger than the initial inflow when it hits the waller 120. Therefore, the flow of combustion air is gradually forced. The phenomenon in which the volume of the combustion air is expanded and the flow is accelerated increases the pressure of the air, and thus has a positive effect on obtaining the swirl flame according to the present invention. As a method of obtaining a high quality swirl flame without sufficiently increasing the amount of inflow of air, this is an unachievable part of the prior art. However, it is also important to note that it is easy to change into turbulence at the inflection point where the direction of air is bent.

The general atmosphere contains 79% nitrogen and 21% oxygen by volume. Nitrogen does not burn. In the present invention, the stability of air for combustion is ensured by using general air containing 79% of nitrogen which does not burn. The reason why the flame does not transfer to the combustion air even though the primary combustion air that hits the outlet side disk 105 and proceeds toward the fuel injection hole 106 is wrapped around the flame and rotates, so that the combustion air contains nitrogen. It is also affected by the distribution ratio of primary combustion air and secondary combustion air. If the oxygen specific gravity is increased by artificially injecting oxygen into the combustion air, the flame will spread to the rotating combustion air, and thus the combustion effect according to the present invention will not be obtained.

The flame around the emulsion injector 130 is formed in a reducing atmosphere in an oxygen deficient state in which oxygen is not sufficient, thereby suppressing generation of NOx. In addition, since water is added to the emulsion, the generation of NOx and SOx is effectively suppressed by this. Emulsion preparation techniques have some rights protected (eg, registration no. 20-0277225), but are almost universal (eg, publication no. 1992-7002486). In the present invention, the emulsion is made in the emulsion injector 130, the proportion of water in the prepared emulsion is 10% to 30% based on the volume. The ratio of water is appropriately adjusted based on the combustion state, the type of fuel, the use of the burner, the degree of NOx and SOx in the exhaust gas, and the like. The emulsion injector 130 is continuously supplied with fuel and water through the fuel hose 132 and the water hose 133 such as diesel fuel, and is automatically cooled so that the emulsion injector 130 can be long-lasted without melting or corrosion by high temperature heat.

The flame exits to the outlet 108 where it encounters secondary combustion air and is completely combusted. Therefore, incomplete combustion residues such as CO, smoke and odor do not occur at all. The flame is also very stable due to the high temperature secondary combustion air.

The outlet 108 is formed in a cylindrical shape and its inner wall surface is constructed of a castable 109. In the burner of the present invention, the castable 109 is struck only by the inner wall of the outlet 108 and the outer disk 105, which is the pressure of the secondary combustion air, and the inner wall of the outer disk 105 and the outlet 108. It is necessary to secure the durability of the outlet side disk 105 and the outlet 108 because it is not enough to form a strong air curtain in the. The diameter of the cylinder in the cylindrical outlet 108 also affects the thickness and intensity of the flame ejected from the burner of the present invention. Therefore, it can adjust suitably according to a use. The cylindrical length of the outlet 108 is also designed to be constant. Since the inner cylinder of the outlet 108 is the secondary combustion chamber, the length of the cylinder also affects the combustion state of the burner according to the present invention. In the basic form, the cylinder length of the outlet 108 is 170 mm.

In the present invention, the burner system may be designed only by removing the middle port 102 and only the outer port 101 and the inner port 103 (hereinafter referred to as 'embodiment 1'). In Embodiment 1, as shown in FIGS. 11 and 12, the blower 111 is installed at the fuel injection side. The inflow and progress of combustion air is the same as in the basic type. In Example 1, since the effect of air cooling is not sufficient, the temperature of the outer wall of the outer port 101 exceeds 80 degrees Celsius, and thus it is safe to make a separate case. Also, the combustion condition is slightly lower than that of the basic type, but is better than the conventional burner. In the case of 'Example 1', the pressure of the blower 111 may be used rather low.

In the present invention, the pressure of the blower 111, the gap between the outer port 101 and the middle port 102, the gap between the middle port 102 and the inner port 103, the diameter and angle of the air nozzle 107 and the outlet If the diameter of 108 is properly designed, it is possible to derive a relatively good combustion state without the emulsion injector 130 (hereinafter referred to as 'Example 2'). Although Example 2 is not shown, fuel is injected into the burner through the fuel injection nozzle. The fuel injection nozzle may be provided in the center of the fuel injection side disk 104 or together with the igniter 140. In 'Example 2', only the oil is used without using the emulsion as fuel, or the emulsion can be made and injected in a device outside the burner. However, the effect of reducing air pollutants is significantly lower than that of the previous type. In particular, in the second embodiment, when the waste oil is operated as a fuel oil for a long time, a problem that non-combustibles such as powder and some soot should accumulate on the bottom of the inner cylinder should be periodically cleaned.

In addition, in the present invention, instead of installing the air nozzle 107, the inner port 103 is supported only by the fuel injection side disk 104 by welding, and the outlet side disk 105 is rotated at the interval by separating at intervals. The air may enter the inner port 103 and hit the outlet side disk 105 to be divided into primary combustion air and secondary combustion air (hereinafter referred to as 'Example 3'). In the third embodiment, a good combustion state can be obtained, but in this case, it is difficult to reduce the diameter of the inner port 103 of the burner, and thus it is difficult to design a burner having a small capacity. In addition, since the air nozzle 107 is not used, it is difficult to properly divide the air for the primary combustion and the secondary combustion air by the angle or the diameter of the air nozzle 107, and thus, the control on the combustion state is very difficult. It is also more difficult to form a strong swirl in the burner. In addition, in the third embodiment, the combustion air rotates inside the inner port 103, and thus, a large cylinder is formed by the centrifugal force, causing friction with the inner wall of the inner port 103 and further increasing the pressure of the air. Increase However, 'Example 3' also can obtain a better combustion state than the existing burner.

As described above, in the present invention, three or two ports 101, 102, and 103 are installed in the burner, and only the normal air is blown at high speed into the burner through the air nozzle 107, and the diesel fuel is passed through the bunker. Emulsion combustion oil mixed with liquid fuel and water such as oil and waste oil is manufactured in the emulsion injector 130 to be injected through the orifice 131, thereby greatly improving combustion efficiency and of course, without using expensive oxygen. It can greatly reduce air pollutants such as NOx, which is a major drawback, and obtain powerful and refined swirling flames.

In particular, high-temperature flames can be obtained even by using emulsion combustion oil in which water is mixed with fuel. The use of water can significantly reduce NOx and SOx and maximize the heat per fuel unit.

In addition, the formation of a reducing atmosphere in an oxygen deficient state upon combustion by air for primary combustion also contributes to the reduction of NOx.

In addition, since dioxins are decomposed by the temperature in the burner being higher than the decomposition temperature of dioxins, dioxins can be volatilized even if waste oil or waste oil refined oils are used, and harmful heavy metals can be volatilized.

When oxygen-depleted flames pass through the outlet, secondary combustion air is supplied, at which time complete combustion occurs and no excess air is injected. Therefore, generation of NOx due to excess air is also suppressed.

In addition, a long and large flame can be obtained as the burner according to the present invention, and can be usefully used as an incinerator or a burner for a kiln.

In addition, the burner according to the present invention, even when using waste oil or waste oil refined oil, the air pollutant comes out below the reference value can significantly reduce the fuel cost or obtain the required amount of heat at the negative fuel cost.

In addition, the burner according to the present invention is characterized in that the ports 101, 102 and 103 of the burner are protected from high temperature by an air curtain by combustion air.

Claims (9)

Burners supported by at least two cylindrical ports 101, 102 and 130 having the same central axis and having different radii, and the discs 104 and 105 on the fuel inlet side and the outlet side supporting the respective ports and discs on the fuel inlet side In the burner consisting of an emulsion injector 130 formed in a cylindrical shape toward the inner central space, the plurality of air nozzles 107 for injecting air from the outer wall surface of the inner port 103 to the inner wall surface are the outer peripheral surface of the inner port 103. Is installed so as to be inclined toward the outlet side disc 105 so that combustion air rotates on the inner wall surface of the inner port 103 and proceeds to the outlet side disc 105, and in the outlet side disc 105 thereon. A part of the colliding combustion air is returned to the burner to make the primary combustion air, so that some of the combustion air exits to the outlet 108 and becomes the secondary combustion air. Burner systems Pollutant reduced. According to claim 1, the emulsion injector 130 has a plurality of orifices 131 perforated to inject fuel around the air for combustion is injected from the emulsion injector 130 while winding the emulsion injector 130 Burner system for reducing air pollutants, characterized by burning fuel The burner system for reducing air pollutants according to claim 1, wherein the fuel injection side disc 104 further includes a waller 120 installed to impart rotational force to the combustion air and adjust the rotation radius. delete delete delete delete delete delete